Rotary vane device with improved seals

ABSTRACT

An eccentric rotor vane device that may be employed as pumps, blowers (or compressors), engines, or motors, characterized by an improved seal structure; in addition to conventional main chamber; first and second ports communicating with the main chamber; a plurality of annularly related radial vanes, independently pivotal and rotatable about a vane axis within the main chamber; a rotor that is eccentrically mounted with respect to the main chamber; a power delivery shaft connected with the rotor. The improved seal means, in specific embodiments, comprises a plurality of cylindrical rollers that serve as vane guides intermediate each pair of adjacent vanes. The cylindrical rollers adjacent each face of each respective vane engages its lateral face such that a satisfactory seal is made as the roller traverses radially inwardly and outwardly along the lateral face of the vane. Thus, the plurality of rollers serve as at least a part of a piston as well as an interdigitating means for effecting a change in volume of a subchamber defined intermediate the respective vanes, rollers, and interior wall in the main chamber. Also disclosed are improved vane structures for maintaining more nearly perfect seals for long service life.

United States Patent [1 Keller ROTARY VANE DEVICE WITH IMPROVED SEALS{75] Inventor: Leonard J. Keller, Sarasota, Fla.

[73] Assignee: The Keller Corporation, Dallas, Tex.

[22] Filed: Oct. ll, 1973 [2]] App]. No: 405,27l

[52] US. Cl 4l8/l37; 4l3/24l [5l] Int. Cl Flllc 1/00; FOlc 19/00; F04C1/00 [58] Field of Search .l 4l8/24l, 136-138,

[56] References Cited UNITED STATES PATENTS LOOQJOO ll/l9ll Haney4l8/24l l,09l,32l 3/l9l4 Fesenbek v. 4l8/l56 2.278.131 3/1942 Livermore4l8/268 3.748.068 7/1973 Keller 418/241 Primary Examiner-C. J. HusarAssistant Examiner-O. T. Sessions Attorney, Agent, or Firm-Wofford,Felsman, Fails & Zobal [451 May 13, 1975 [57] ABSTRACT An eccentricrotor vane device that may be employed as pumps, blowers (orcompressors), engines. or mo tors. characterized by an improved sealstructure; in addition to conventional main chamber; first and secondports communicating with the main chamber; a plurality of annularlyrelated radial vanes, independently pivotal and rotatable about a vaneaxis within the main chamber; a rotor that is eccentrically mounted withrespect to the main chamber; a power delivery shaft connected with therotor. The improved seal means, in specific embodiments. comprises aplurality of cylindrical rollers that serve as vane guides intermediateeach pair of adjacent vanes The cylindrical rollers adjacent each faceof each respective vane engages its lateral face such that asatisfactory seal is made as the roller traverses radially inwardly andoutwardly along the lateral face of the vane. Thus, the plurality ofrollers serve as at least a part of a piston as well as aninterdigitating means for effecting a change in volume of a subchamberdefined intermediate the respective vanes, rollers, and interior wall inthe main chamber. Also disclosed are improved vane structures formaintaining more nearly perfect seals for long service life.

6 Claims, 4 Drawing Figures ROTARY VANE DEVICE WITH IMPROVED SEALSBACKGROUND OF THE INVENTION l. Field of the Invention This inventionrelates to an improvement in eccentric rotor, concentric vane devicesthat may be employed as pumps for pumping incompressible fluids, blowersfor compressing and pumping compressible fluids, as engines powered byinternal combustion ofa fuel using either spark ignition cycle or thediesel cycle, or as motors powered by compressible or partiallyincompressible fluids.

2. Description of the Prior Art Eccentric rotor, concentric vane deviceshave been known at least since the middle of the l9th century; US. Pat.Nos. 43,744 and 83,186 being granted, re-. spectively, in l864 and 1868on rotary steam engines. Subsequently, there has been at least eighteendifferent United States patents issued on similar structures for one ormore of the uses delineated hereinbefore. Yet, not a single one of thepatented devices, insofar as I am aware, has achieved widespreadcommercial use. The failure to be widely useful is generally conceded tobe due to lack of having a satisfactory seal between the vanes and thevane follower, or vane guide, portion of the rotor that interdigitatesthe vanes. The seal means attempted before my invention have eitherallowed too much leakage to be practical or have imposed too muchfrictional resistance to movement to allow the machines sufficientmechanical efficiency to be practical. The early attempts; theintermediate attempts, such as exemplified by US. Pat. No. 2,129,43l;and very recent attempts, such as delineated in US. Pat. No. 3,572,985,employed semicylindrical seal members slidably engaging each side ofplanar vanes as they slid radially inwardly and outwardly along thevanes. Other patents, such as US. Pat. No. 2,022,209, describedemploying a seal having a knife-like edge that engaged planar vanes,attempting to seal as it moved radially inwardly and outwardly along thevanes. None effected the desired satisfactory seal. In my US. Pat. No.3,748,068, I delineated an improved seal structure that solved theproblems of the prior art; including the art cited in that patent. Withexperience in different embodiments, alternative seal structures havebeen found to be equally efficacious and provide unobvious advantagesover the prior art. For example, it has been found desirable to provideindependent rolling friction intermediate respective rollers contiguousrespective vane faces for effecting a low frictional drag and long life.

Accordingly, it is an object of this invention to provide an eccentricrotor vane device that obviates the disadvantages of the prior artstructure.

Specifically, it is an object of this invention to provide an eccentricrotor vane device having an improved seal between the interdigitatingportion of the rotor and adjacent vanes throughout the full 360 ofrotation of the rotor such that the interdigitating portion can operateas a piston, as well as a vane guide and employ rolling frictionintermediate a roller contiguous each adjacent face of each vane;regardless of whether the rotor vane device is being employed as a pump,blower, engine or motor.

It is also an object of this invention to provide a rotor vane devicehaving the same advantages as delineated in US. Pat. No. 3,748,068 andstill provide the foregoing objects.

These and other objects will become apparent from the descriptive matterhereinafter, particularly when taken in conjunction with the drawings.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partial cross sectionalview from the side of one embodiment of this invention.

FIG. 2 is a partial cross sectional view from the side showing a sleeveserving as an internal wall in the main chamber, rotor, vanes, vaneguides, and the respective seals therebetween in accordance with anotherembodiment of this invention.

FIG. 3 is a partial cross sectional view from the side showing a sleeve,rotor, vanes, vane guides, and the re' spective seals therebetween inaccordance with another embodiment of this invention.

FIG. 4 is a partial cross sectional view from the side showing a sleeve,rotor, vanes, vane guides and the respective seals therebetween inaccordance with still another embodiment of this invention.

DESCRIPTION OF PREFERRED EMBODIMENTS Referring to FIG. I, there isillustrated one embodiment of this invention in the form of a motor 11,or eccentric rotor, concentric vane motor device. The motor 11 comprisesa stator I3; a rotor, or rotor assembly, 15; and a vane assembly 17. Themotor 11 is described in detail in my copending patent applicationentitled Rotor Vane Motor Device", Ser. No. 227,393, filed Feb. I8,1972, now Pat. No. 3,797,975; and the descriptive matter containedtherein is embodied by reference herein for complete description of theconstruction and operation of the motor. In that application, the motordescribed was a variable torque, vairable power motor employing theimproved seals described in my aforementioned US. Pat. No. 3,748,068;and having improved torque and power control means. The de scriptivematter of US. Pat. No. 3,748,068 is also incorporated herein byreference. In view of the aforementioned U.S. Pat. No. 3,748,068 and thepatent application Ser. No. 227,393, now US. Pat. No. 3,797,975, thefollowing abbreviated description is believed adequate and is affordedmerely for the convenience of the reader to prevent having to refer tothe delineated patent and patent application.

The stator l3 includes a main body member 19 having a base or mountingbracket 21. The main body member 19 has peripherally disposed circularflanges (not shown) for affixing cap members at each side of the motor11, or each end of a main chamber. A longitudinal cylindrical cavity 23is formed in the inner face of the main body member 19 and includes amain chamber. An inlet port 25 is formed in the inner face of the mainbody member 19 and extends from the medial top, or 0, position thereoffor about 50 clockwise. The inlet port 25 has its leading and trailingedges 27 and 29 extending longitudinally for the full length of the mainbody member 19 for providing maximum flow area. The inlet port 25communicates via passageway 31 in main body member 19 with a collar 33to facilitate connecting an inlet of motor 11 with a high pressuresource of working fluid, as described in detail in Ser. No. 227,393, nowUS. Pat. No. 3,797,975. Similarly formed in the inner face ofthe mainbody member 19 is an exhaust, or discharge, port 35. The discharge port35 has a leading edge 37 that extends longitudinally of the longitudinalcylindrical cavity 23 and main body member 19, and that is spaced about25 peripherally thereof from the trailing edge 29 of the inlet port 25.The discharge port 35 also has a trailing edge 39 that extendslongitudinally of the longitudinal cylindrical cavity 23 and trails theleading edge 37 by approximately 90. The discharge port 35 communicatesvia passageway 41 in the main body member 19 with a collar 43 tofacilitate connection with a low pressure receiver, as described in theaforementioned Ser. No. 227,393 now US. Pat. No. 3,797,975.

The pair of cap members at each side of the main body member 19 andtheir attachments thereto is described in detail in Ser. No. 227,393,now US. Pat. No. 3,797,975. Similarly described therein, are themechanical accessories enabling rotation of the rotor and its shaft. Thedescribed accessories include; for example, the coaxial bearing sleevesthat are integrally formed with the cap members; the thrust plate thatis secured to the bearing sleeve by cap screws with a seal therebetween;the coaxial collar that is secured by cap screws to the outer end of thebearing sleeve and dis posed about the rotor shaft extendingtherethrough; together with the respective shaft seals and bearings.

As described in the above referenced Ser. No. 227,393, now US. Pat. No.3,797,975, the end caps also define exhaust or discharge chambersdisposed longitudinally exteriorly of the openings in respective annularplates 49 disposed annularly about the rotor assembly 15, the latterbeing described in more detail hereinafter. The annularly disposedplates 49, as illustrated, have a plurality of discharge apertures 85for discharging the fluid. The respective annularly disposed plates 49may be rotated by suitable pinion gear or the like (not shown) toadvance or retard the second set of discharge apertures 85 for furtherrefinement in torque control, similarly as described in Ser. No.227,393, now US. Pat. No. 3,797,975.

The rotor assembly includes a pair of opposite and mating circularplates 45 at each end. The plates 45 engage, or proximate, the circularapertures 47 in the annularly disposed plates 49. If desired, bearingmaterials can be provided at the interface between the respectivecircular plates 45 and the inner walls of the apertures 47. The followermeans, such as the vane guides 51, are retained intermediate theoppositely disposed faces of the circular plates 45 at each end of therotor 15. The vane guides 51 serve as both pistons and means forinterdigitating the vanes. thereby effecting a change in volume ofsubchambers 53 intermediate the respective adjacent vanes as the rotorassembly and the vanes are rotated within the main chamber. Eachsubchamber 53 is defined by a pair of confronting vane faces on itssides, a vane guide 51 and an interior surface 55 of a torque controlsleeve 57 at its radially inner and outer boundaries, and the annularplates 49 at its ends. Each subchamber 53 varies from a minimum volumeat the outermost, or 0, position of the vane guide 51 to a maximum atthe innermost, or 180, position of the vane guide 51. The vane guide 51traverses inwardly and outwardly radially along the adjacent vanes toeffect the improved seal that makes practical this inven tion, asdescribed later hereinafter in more detail with respect to the vanes andthe vane assembly.

Each of the illustrated follower means comprises a vane guide 51 thatextends longitudinally along the rotor with vane engaging surfacecontiguous the lateral face of the vane. As illustrated, each vane guidecomprises a plurality of cylindrical rollers 59 that are rotatablymounted on a shaft 61. Rotation of each cylindrical roller 59 isfacilitated by suitable bearing means, such as insert 63. As illustratedand described in U.S. Pat. No. 3,748,068, each shaft 61 is fixed betweenshoulders (not shown) of the circular plates 45 by cap screwspenetrating through apertures in the circular plates.

As indicated hereinbefore and as described in US. Pat. No. 3,748,068, apower shaft 65 is affixed to and extends coaxially from the circularplates 45 to the respective roller bearings in the bearing sleeves inthe respective ends (all not shown). As indicated, the shaft 65 of motor11 is journalled within coaxial collars and shaft seals and extendsoutwardly to deliver, as by way of suitable coupling means, power tousing apparatus. If the device 11 is being employed as a pump or blower,the shaft delivers power to the rotor 15.

The respective coupling means may be any of the conventional couplingmeans, including but not limited to linear in-line couplers, gearreducing couplers, or properly sized sheaves and endless member drives;such as belts or chains. As in conventional practice, one end of thecoupling means will be connected with the shaft; as by key and slotcombination, or splines (not shown).

A second shaft also extends coaxially from the opposite circular plate45 and is journalled for rotational movement in its roller bearings inbearing sleeves to provide additional support for the rotor assembly 15.

As described in Ser. No. 227,393, now US. Pat. No. 3,797,975, each ofthe shafts 65 has a male threaded portion that threadedly engages atapped aperture in respective circular plates 45 when the shafts arethreaded into tapped apertures, respective shoulders are pulled intotight engagement with the exterior of the respective circular plates 45to form a strong connections therebetween. The threads are formed suchthat they are not loosened in normal rotation. Respective sets of rollerthrust bearings are provided intermediate the exterior of the respectivecircular plates 45 and the adjacent end caps (not shown). if desired,thrust bearings may be counter sunk to keep the clearance intermediatethe plates to a minimum. Preferably, aircraft type roller bearings areemployed as thrust bearings, although other bearings may be employed asappropriate to the use of the device, or motor 11. Bearings provideimproved structure and should not be omitted casually.

The rotor assembly 15 is eccentrically disposed within the longitudinalcavity 23, and its power shaft 65 is eccentric with respect to thecentral axis of the longitudinal cavity 23.

The vane assembly 17 is located in a vane assembly cavity 67 that isdefined by the sleeve 57 concentrically within the longitudinal cavity23. The vane assembly 17 includes a floating axle pin, or shaft, 69 thatis substantially coaxial with the longitudinal cavity 23 and extendsbetween the circular plates 45 of the rotor assem bly 15. A plurality ofvanes 71 extend radially outwardly from the axial pin 69 and areindividually pivotal thereon. As illustrated, each vane is provided witha curved end plate 73 of substantially the same radius of curvature asthe inner surface 55 of the sleeve 57. The curved end face 73 of eachvane is in substantial sliding engagement with the sleeve 57 such thatit forms a satisfactory seal for confining the fluid in the respec tivesubchambers 53 on either side thereof. The seals intermediate the vanes71 and the sleeve 57 have not been particularly critical because thedifferential pressure between adjacent subchambers 53 is notinordinately high and because the centrifugal force on the vanes 71tends to retain sufficient sealing engagement between the respectivevane ends 73 and sleeve 57. Any type of seal appropriate to the vaneends 73 may be employed, as described in the aforementioned Ser. No.227,393 now U.S. Pat. No. 3,797,975 and U.S. Pat. No. 3,748,068. Theradially exterior end 73 of the respective vanes may be formed asdesired to minimize the volume in the subchamber defined between theradially outermost ends of adjacent vanes. For example,

the vanes 71 may have arcuate intruding shoulders to more closely fitthe respective plurality of cylindrical rollers 59 of the rotor assemblyto reduce the volume to near Zero.

As described in detail in Ser. No. 227,393 now U.S. Pat. No. 3,797,975,each of the vanes 71 has integrally formed with the inner radial endthereof at least one annular knuckle 75 that conformingly engages theaxle pin 69. The knucles 75 of respective vanes 71 are axially offsetrelative to each other along the axle pin 69 and are stacked on the axlepin with their confronting faces in sliding engagement to permit therelative interdigitating, or rocking, of the vanes 71 about the axle pin69. It will be appreciated that; as specifically illustrated in theaforementioned U.S. Pat. No. 3,748,068; the vane central knuckle istwice as wide as ordinary and disposed intermediate the adjacentknuckles on either side. If desired, the vanes may have the respectiveknuckles disposed at one-half of the axle pin 69 plus the thickness ofone knuckle and intermesh such that the use of the wide central knuckleis obviated. Any other method of supporting the vanes that will allowthe interdigitating thereof may be employed. Since the vanes areaccelerated and decelerated during rotation, however, symmetricalarrangement of the knuckles with respect to a transverse plane throughthe vanes center is preferable.

The respective vanes 71 have lateral faces 77 that are concaved inwardlytoward the central plane of the vane such that the respective followers,or vane guides, 51 are maintained in substantially uniform sealingengagement with the vane lateral faces 77 as the vane guides 51 traverseradially inwardly and outwardly therealong during rotation of the rotorassembly 15. By substantially uniform sealing engagement is meant anengagement such that a satisfactory seal is maintained intermediate therespective vane guides 51 and the vanes 71 so that the vane guides 51can serve as pistons as well as interdigitating means as they traverseradially inwardly and outwardly along the respective vanes 71.

As is well recognized, what is satisfactory sealing engagement will varydepending upon the application, or use; which determines severalpertinent factors. These factors include the size of the unit, thedifferential pressure across a vane guide 51 from the subchamber to theinterior of the rotor assembly 15, the total pressure of the fluid beinghandled in the subchamber and the efficiency desired. To illustrate, Ihave found that as much as 0.010 inch clearance may be tolerated betweenthe vane guides 51 and the vane lateral faces 77 with large motors suchas may be employed with low pressure steam. For example, with lowpressure steam that may be emitted from geothermal wells, the motordevice may have dimensions as large as 30 inches in length by 36 inchesin diameter; or larger, if used on individual steam wells. On the otherhand, when employing the motor with a low entrophy fluid flowingtherethrough, l have found it preferable that a clearance of less than0.005 inch; for example, about 0.00l-0.003 inch; be employed between thesurfaces of the vane guides 51 and the vane lateral faces 77. Lightermotors may be only about 4 inches in length and 6 inches in diameter,yet develope enough power to operate a small automo bile.

The improved seal means of this invention, as de scribed hereinbelow,makes practical the eccentric r0 tor, concentric vane motor of thisinvention, that has all of the advantages of the invention of U.S. Pat.No. 3,748,068 and the aforementioned Ser. No. 227,393 now U.S. Pat. No.3,797,975. This improved seal preferably employs a plurality that is aneven number of cylindrical rollers 59 intermediate each pair of adjacentvanes 71. By this structure, each of the rollers 59 engages respectivelateral faces 77 of the vane contiguous therewith, as well as engage thesurface of any adjacent cylindrical roller 59 with rolling friction.Thus, reduced friction is effected for more efficient operation.Moreover, there is substantially no wear and the wear is evenlyapportioned, because of the rolling interconnection between contiguoussurfaces, the rolling of contiguous surfaces being in the samedirection, or compatible rather than opposite, for still less friction.Consequently, the improved seal means is durable and trouble-free, thecylindrical rollers rolling along the vane faces and in contact witheach other.

As noted in U.S. Pat. No. 3,748,068 and Ser. No. 227,393 now U.S. Pat.No. 3,797,975, I have attempted to delineate, through mathematicalexperts and computer computations, the exact definition of the concavity of the lateral faces 77 but have not been successful to date. Theconcavity can be delineated graphically, employing a scale that islarger than actual size. I have developed an empirical formula bytrigonometry which is close also. In practice, I have found exactmathematical delineation to be unnecessary. Instead, I employ a grindingjig with grinding rollers to duplicate the physical relationships anddimensions employed in a particular motor device 11. Specifically, thegrinding of the vane faces is effected by repeatedly moving the vanesand sized grinding rollers through 360' as the vanes are moved by therotor assembly 15, with increasing distances of eccentricity up to theeccentricity actually employed in the motor device 1]. By increasingdistances of eccentrically is meant the increasing moving apart, withsuccessive revolutions, of the shaft of the vane axle pin 69 and theaxis of the shaft of the grinder rollers that is equivalent to the axisof the shaft of the rotor assembly 15, as described in Ser. No. 227.393now U.S. Pat. No. 3,797,975. In this way, I get exact in itialengagement and do not have to worry about the clearance. Once aparticular vane contour, or concavity, has been established for aparticular motor, it may be reproduced by conventional methods ofcopying.

In the above referenced Ser. No. 227,393 now U.S. Pat. No. 3,797,975,there was described an integral adjusting flow through and torquecontrol means for controlling torque output of the motor 11 so that itcould be operated without requiring a throttle and the throttle-causedlosses in efficiency. That does not comprise a part of this invention,per se, and need not be described in detail herein. It is sufficient tonote that the flow through and torque control means comprises the torquecontrol sleeve 57, delineated hereinbefore, that is conforminglydisposed interiorly of the longitudinal cylindrical cavity 23. Thetorque sleeve 57 mates with and telescopes within the cavity 23 androtatably and slidably engages the inside face of the cavity to permitangular adjustment of the torque control sleeve 57. The torque controlsleeve has at least an inlet aperture in the form of a first set oflongitudinally extending slots 79. The inlet slots 79 communicatebetween the interior of the vane assembly cavity 67 and the inlet port25. It is sufficient to note in the abbreviated description herein thatadvancing of the torque control sleeve by suitable gear 81 will increasethe effective flow area through the inlet apertures until the inletaperture is at a maximum. On the other hand, the torque control sleeve57 may be retarded or rotated in a second direction opposite the firstdirection to decrease the effective flow area of the inlet aperture andinlet port. The degree of retardation may be sufficient to completelyclose off the inlet port or to effect a reduced flow of fluid throughthe motor. The respective means for controlling the gear 87 is describedin detail in Ser. Nov 227,393 now U.S. Pat. No. 3,797,975 and is notshown or described herein.

Also, the use of discharge slots 83 to control the dis chargeindependently for reducing losses from over expansion or under expansionof a working fluid flowing through the motor 11 was described in detailin Ser. No. 227,393 now U.S. Pat. No. 3,797,975.

In operation, a fluid will enter through the inlet passageway 31 andinlet port 25, entering into the respec tive subchambers 53 at theirminimum volume position near the top. The point of entry may becontrolled by the torque control sleeve 57. The fluid is preferably anexpansible fluid that will do work as it expands to effect rotation ofthe respective vanes and act against the respective vane guides, orplurality rollers 59, serving as a piston. This forces rotation of therotor assembly and the work output shaft as the fluid expands to themaximum position near the bottom. Shortly past the bottom, the fluidwill be vented through a second set of discharge apertures 85 in theannularly disposed plates 49, or through the discharge slots 83 anddischarge port 35, depending upon which are set earlier by therespective torque control means. Thus, as each subchamber is rotated,the fluid contained therein is allowed to do work and deliver power fromthe motor 11 before the fluid is begun to be discharged in its fullyexpanded condition directly to the pressure existing in the dischargepassageway 41, without any throttle control losses. The respectivesealing surfaces on the respective plurality of rollers 59 remaincontiguous and in sealing engagement with a rolling action to minimizefriction and wear.

Another embodiment of this invention is illustrated in FIG. 2. Therein,only a portion of the torque control sleeve 57 is illustrated since theenvironment is the same as described hereinbefore with respect toFIG. 1. As illustrated in FIG. 2, each respective vane guide 51comprises two cylindrical rollers 59A and 598 that are affixed by theirrespective shafts 61 to the circular plates 45, similarly as describedhereinbefore. As illustrated in FIG. 2, however, the respectiveplurality of rollers 59A and 59B are not contiguous each other, but arecontiguous an intermediate member 87. Specifically, the respectivecylindrical rollers 59A and 59B engage the respective seals 89 and 91that are sealingly engaged in recesses in the coextensive andlongitudinally extending intermediate member 87. Expressed otherwise,the intermediate member 87 extends coextensive with the respectiverollers 59A and 59B longitudinally of the rotor assembly 15 and issealingly affixed to the circular plates 45, similarly as are the shafts61 of the rollers.

As illustrated, the respective vanes 71 have their vane lateral faces 77contoured to maintain the desired sealing engagement with the surfacesof the respective rollers 59A and 598, as described hereinbefore withrespect to the lateral faces 77 of the vanes 71. Otherwise, thestructure of the vanes, with their axle pin 69; the vane assembly 17;the rotor assembly 15; the main body member 19 and the respective inletand discharge ports 25 and 35 are the same and the operation is the sameas described with respect to the embodiment of FIG. 1.

Thus, it can be seen that in the embodiment of FIG. 2, the respectiverollers 59A and 59B engage their respective contiguous vane lateralfaces 77 with a rolling action as the vane guides 51 move radiallyinwardly and outwardly along the vanes 71. This rolling action attainsthe desired lowered friction and reduced wear, similarly as describedhereinbefore with respect to the embodiment of FIG. 1. If desired, theintermediate memberr 87 may have a plurality of roller bearings forsealingly engaging the rolling surface of the respective cylindricalrollers 59A and 593, instead of or in addition to the respective seals89 and 91.

Still another embodiment of the invention is illustrated in FIGS. 3 and4. In FIG. 3, the same embodiment about the torque sleeve 57 is employedas described with respect to FIG. 1. Similarly, the same cylindricalrollers 59 are employed as the vane guides 51, as described with respectto FIG. 1. In the embodiments of FIGS. 3 and 4, however, each vane 71comprises first and second members 93 and 95 that are biased towardtheir respective contiguous rollers 59 for maintaining the satisfactorysealing engagement there with. Respective first and second members maycomprise simply a bifurcated end of an integral vane in which thephysical properties of the material of which the vane is made biases thefirst and second members toward their respective rollers 59. Asillustrated, how ever, the second member 95 is pivotally mounted suchthat its radially outermost end is biased away from the radiallyoutermost end of the first member 93. The pivotal mounting may comprisesimply a quasi-cylindrical head 97 that is embedded in a suitable slot99 in the main body of the vane, with or without an inherent bias beingeffected. On the other hand, one or both of the first and second membersmay be sealingly mounted on a fulcrum shaft if desired. Sealing of thequasicylindrical head in a conforming slot 99 is more easily effected.It is apparent, however, that the use of a vane 71 having a bifurcatedend forming the first and second members 93 and 9S automatically effectssealing and overcomes the problem with sealing, although it isrelatively expensive to form the slot intermediate the bifurcatedmembers.

In the embodiment of FIG. 3, the first and second members have a springmember 101 seated in respective recesses 103 and biasing the radiallyoutermost ends of the respective vanes 71 toward their respectivecontiguous rollers 59.

in the embodiment of FIG. 4, the space intermediate the respective firstand second members 93 and 95 is filled with a compressible material foreffecting the biasing of the radially outermost ends of the vanes 71toward their respective contiguous rollers 59. As illustrated, thecompressible material is the compressible fluid that is being flowedthrough the motor 11, FIG. 1. If desired, the compressible material maybe a resilient material such as the elastomeric materials like rubber.The elastomeric material should be resistant to the fluid being flowedthrough the motor. For example, the synthetic rubbers like Neoprene orBuna N, may be employed satisfactorily.

The embodiments of FlGS. 3 and 4 operate similarly as describedhereinbefore with respect to the embodiments of FIGS. 1 and 2. It isnoteworthy, however, that good sealing contact is made because of theflexibility and the biasing of the bifurcated first and second memberstoward their respective contiguous rollers 59. The resulting compressiveforce exerted on the contiguous rollers 59 also assists in maintainingsealing contact between the respective surfaces of the rollers as weardevelops between the respective shafts and inserts 6i and 63.

The operation of the motor 11 as a pump or air compressor is describedin the hereinbefore referenced U.S. Pat. No. 3,748,068 and thatdescriptive matter need not be repeated herein.

The materials of construction ordinarily employed in this art may beemployed herein and no exotic new materials are necessary. Thestructural strength and the wearing properties of the materials thatinterface together will be chosen appropriate to the application. Forexample, in certain applications it may be possible to employ plasticsto reduce the friction as they interface with adjacent metalliccomponents. In general, we have been working with the most deleterioustypes of materials, such as steam, and have employed noncorrodablemetals in those surfaces in contact with such materials, or fluids.

It is noteworthy that when the device is employed as an air compressor,or blower, similarly as described in U.S. Pat. No. 3,748,068, it hasmany advantages that are not found in the ordinary blowers. For example,in centrifugal blower embodiments, there is no problem of balancing;since the rotor assembly 15 may be run with up to several poundsout-of-balance mass in the larger sizes. This is in contrast to only afew ounces, or less of imbalance that is tolerable in conventionalblowers. For example, I have designed a large diameter unit to serve asa centrifugal blower that will deliver up to five million standard cubicfeet per minute of air for use in magneto hydrodynamics applications.There is no conventional blower that can presently supply this amount ofair. The use of rolling friction with the improved plurality ofcylindrical rollers enables employing large size units withoutintolerable friction.

From the foregoing, it can be seen that a highly eff"- cient positivedisplacement device is provided that iinally achieves all of theadvantages heretofore known but not practically achieveable because ofthe difficulty with seals intermediate the rotor assembly and the vanes.Specifically, this invention provides a rotor vane device that achievesthe objects delineated hereinbefore and obviates the disadvantages ofthe prior art devices. lts size and weight are unbelieveably morecompact and lighter than conventional air compressors. The use of rollervane guides, with the attendant rolling friction, effects along-wearing, trouble-free seal that is an important advance in thetechnology to improve our ecology. The rotor vane device also makespractical an essentially nonpolluting engine that may be used as anexpander in an external combustion Rankine cycle system.

Moreover, as disclosed in U.S. Pat. No. 3,748,068, the large changes involume of the subchambers allow unusually large variation in compressionratios when the rotor vane device is employed as an engine.

Also, the numerous advantages of the motor 11 are described in the abovereference Ser. No. 227,393 now U.S. Pat. No. 3,797,975. These numerousand lengthy advantages are not repeated herein, although this inventionalso provides these same advantages over the art prior to the abovedescribed Ser. No. 227,393 new U.S. Pat. No. 3,797,975.

A wide variety of other embodiments employing the basic improved sealare feasible. Only a few of the different embodiments are implicit andexplicit in the descriptive matter hereinbefore. it would be virtuallyimpossible to catalogue all of the embodiments. Hence, although thisinvention has been described with a certain degree of particularity, itis understood that the present disclosure has been made only by way ofexample and that numerous changes in the details of construction and thecombination and arrangement of parts may be resorted to withoutdeparting from the spirit and the scope of this invention.

What is claimed is:

1. In an eccentric rotor vane device having:

a. a main chamber having a substantially cylindrical interior surface;

b. first and second ports spaced around and communicating with said mainchamber;

0. a plurality of annularly related radial vanes, independently pivotaland rotatable within said main chamber about a vane axis therewithin;said vanes occupying substantially the total radial distance from saidaxis to said interior surface of said main chamber;

(1. a rotor that is eccentrically mounted with respect to said mainchamber and rotatable about a rotor axis spaced from said vane axis;said rotor having follower means for interdigitating said vanes andeffecting a change in volume of a subchamber intermediate respectivesaid vanes as said rotor and said vanes are rotated within said mainchamber; each subchamber being delineated by a pair of confronting vanefaces and a corresponding follower means between said vane faces andsaid main chamber interior surface and varying from a minimum volume ata radially outermost position of said follower means with respect tosaid vane axis, said minimum volume position being referred to as the 0position, to a maximum volume at the radially innermost position of saidfollower means, referred to as the position; and

e. power delivery shaft connected with said rotor for delivering powerin association therewith; the improvement comprising an improved sealmeans intermediate said vanes and said follower means in which:

fr each follower means is disposed intermediate adjacent said respectivevanes and comprises a plurality of rotatably-mounted cylindrical rollersextending longitudinally of said rotor; each said roller havingrespective vane engaging surface; said plurality of said rollersintermediate adjacent vanes being contiguous each other; and g. saidvanes have lateral faces that are concaved inwardly toward the centralplane of the vane such that said follower means is maintained insubstantially uniform sealing engagement with said vane lateral faces assaid follower means traverse inwardly and outwardly therealong duringrotation of said rotor such that a satisfactory seal is maintainedintermediate said follower means and said vanes so that said followermeans can serve as a pistonas well as an interdigitating means; and eachsaid to]- ler contiguous a lateral face of a vane engages said vane facewith rolling friction for reduced friction and long life.

2. The device of claim I wherein said plurality of rollers intermediateadjacent vanes is an even number of rollers such that said rollersengage said vanes and each other with rolling friction.

3. The device of claim 1 wherein each said vane comprises first andsecond vane members that are biased toward their respective contiguousrollers for maintaining satisfactory sealing contact therebetween.

4. The device of claim 3 wherein said first and second vane members havea spring member disposed therebetween for effecting the biasing.

5. The device of claim 3 wherein said first and second vane members havea compressible material disposed therebetween for effecting the biasing.

6. The device of claim 5 wherein said compressible material is acompressible fluid.

1. In an eccentric rotor vane device having: a. a main chamber having asubstantially cylindrical interior surface; b. first and second portsspaced around and communicating with said main chamber; c. a pluralityof annularly related radial vanes, independently pivotal and rotatablewithin said main chamber about a vane axis therewithin; said vanesoccupying substantially the total radial distance from said axis to saidinterior surfaCe of said main chamber; d. a rotor that is eccentricallymounted with respect to said main chamber and rotatable about a rotoraxis spaced from said vane axis; said rotor having follower means forinterdigitating said vanes and effecting a change in volume of asubchamber intermediate respective said vanes as said rotor and saidvanes are rotated within said main chamber; each subchamber beingdelineated by a pair of confronting vane faces and a correspondingfollower means between said vane faces and said main chamber interiorsurface and varying from a minimum volume at a radially outermostposition of said follower means with respect to said vane axis, saidminimum volume position being referred to as the 0* position, to amaximum volume at the radially innermost position of said followermeans, referred to as the 180* position; and e. power delivery shaftconnected with said rotor for delivering power in association therewith;the improvement comprising an improved seal means intermediate saidvanes and said follower means in which: f. each follower means isdisposed intermediate adjacent said respective vanes and comprises aplurality of rotatably-mounted cylindrical rollers extendinglongitudinally of said rotor; each said roller having respective vaneengaging surface; said plurality of said rollers intermediate adjacentvanes being contiguous each other; and g. said vanes have lateral facesthat are concaved inwardly toward the central plane of the vane suchthat said follower means is maintained in substantially uniform sealingengagement with said vane lateral faces as said follower means traverseinwardly and outwardly therealong during rotation of said rotor suchthat a satisfactory seal is maintained intermediate said follower meansand said vanes so that said follower means can serve as a piston as wellas an interdigitating means; and each said roller contiguous a lateralface of a vane engages said vane face with rolling friction for reducedfriction and long life.
 2. The device of claim 1 wherein said pluralityof rollers intermediate adjacent vanes is an even number of rollers suchthat said rollers engage said vanes and each other with rollingfriction.
 3. The device of claim 1 wherein each said vane comprisesfirst and second vane members that are biased toward their respectivecontiguous rollers for maintaining satisfactory sealing contacttherebetween.
 4. The device of claim 3 wherein said first and secondvane members have a spring member disposed therebetween for effectingthe biasing.
 5. The device of claim 3 wherein said first and second vanemembers have a compressible material disposed therebetween for effectingthe biasing.
 6. The device of claim 5 wherein said compressible materialis a compressible fluid.